WO2002068250A1 - Soupape, notamment pour des systemes de freinage hydrauliques de vehicules - Google Patents

Soupape, notamment pour des systemes de freinage hydrauliques de vehicules Download PDF

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Publication number
WO2002068250A1
WO2002068250A1 PCT/EP2002/001385 EP0201385W WO02068250A1 WO 2002068250 A1 WO2002068250 A1 WO 2002068250A1 EP 0201385 W EP0201385 W EP 0201385W WO 02068250 A1 WO02068250 A1 WO 02068250A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
force transmission
transmission element
housing
valve according
Prior art date
Application number
PCT/EP2002/001385
Other languages
German (de)
English (en)
Inventor
Christoph Voss
Original Assignee
Continental Teves Ag & Co. Ohg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10141135A external-priority patent/DE10141135A1/de
Priority claimed from DE10141136A external-priority patent/DE10141136A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Priority to DE50206891T priority Critical patent/DE50206891D1/de
Priority to JP2002567584A priority patent/JP2004526617A/ja
Priority to EP02727322A priority patent/EP1363820B1/fr
Priority to US10/467,730 priority patent/US7055796B2/en
Publication of WO2002068250A1 publication Critical patent/WO2002068250A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/369—Valves using piezoelectric elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
    • F16K31/007—Piezo-electric stacks

Definitions

  • the invention relates to a valve, in particular for hydraulic motor vehicle brake systems, according to the preamble of patent claim 1.
  • a valve with a piezo drive is already known from DE 199 46 827 Cl, which has a valve member with an actuating piston and an actuating piston for controlling liquids. Between the actuating piston and the actuating piston there is a hydraulic chamber which acts as a hydraulic coupler and which acts on an annular piston and the actuating piston. The differently sized end faces of the ring piston and the actuating piston result in a stepped translation of the stroke initiated by the piezo drive.
  • the valve should also be universally applicable and have the best possible, simple internal seal. Furthermore, this valve should have a steady and comfortable operating behavior regardless of temperature fluctuations and with a relatively simple structure.
  • FIG. 1 shows a first embodiment of the invention for a valve open in the basic position
  • FIG. 2 shows a second embodiment of the invention for a valve closed in the basic position
  • Figure 3 shows a third embodiment of the invention for a valve open in the basic position, which has temperature compensating means.
  • valve tappet 4 which is guided in a valve housing 5 and has a valve closing member 6 at one end.
  • the valve closing member ⁇ is a nem in the valve housing 5 integrated valve seat 7, wherein the valve closing member 6 is actuated indirectly by means of a piezo element 1.
  • a first and a second force transmission element 2, 3 are arranged between the piezo element 1 and the valve tappet 4, the first force transmission element 2 consisting of a high-strength material which, when the piezo element 1 is electrically activated, elastically deforms the second force transmission element 3 and it moved towards the valve lifter 4.
  • the contact area A2 of the second force transmission element 3 that is in contact with the end face of the valve tappet 4 is smaller than the contact area A3 of the second force transmission element 3 that is elastically deformable for stepless translation Construction mentioned in the introduction that the second force transmission element 3 seals the hydraulically loaded inner region of the valve housing 5 against the dry inner region of the valve housing 5 in a simple and absolutely safe manner, for which purpose the second force transmission element 3 is advantageously made of an elastomer, ⁇ . B. from commercially available rubber, or a silicone.
  • the second force transmission element 3 can be pretensioned particularly simply by the choice of the setting depth of the piezo element 1 in the valve housing 5 in order to realize the required sealing effect of the second force transmission element 3 as well as the desired basic setting of the valve tappet 4.
  • the piezo element 1 is supported with its end face facing away from the first force transmission element 2 on a cover 24 which closes the valve housing 5 and which is used for. Setting the piezo element 1 in the valve housing 5 is displaceable.
  • the cover 24 is, for example, with the sleeve section of the valve. tilgebliuses 5 welded.
  • non-positive and / or positive locking options for the cover 24 are also conceivable.
  • the piezo element 1 is designed as a stacked piezo block, and the first force transmission element 2 is designed as a piston guided along the inner wall of the valve housing 5, which rests on the second force transmission element 2 designed as a cushion.
  • the proposed structure of the valve also enables in the closed basic position of the valve closing member 6 to sense the hydraulic pressure applied to it, since via the two force transmission elements 2, 3 there is a hydraulic reaction to the piezo element 1, the electrical voltage change resulting from the mechanical pressure stress by means of a electronic evaluation unit can be converted into a pressure value.
  • the valve according to FIG. 1 shows a valve housing 5 consisting of two housing sleeves 5a, 5b which are joined together in sections and which are connected to one another in the joining area by means of a welded connection 9.
  • the lower housing sleeve 5b is designed as a stepped housing pot, the edge 10 of which is bent at right angles to the outside is caulked in the stepped receiving bore 11 of a block-shaped valve carrier 12.
  • This housing pot has at its bottom a first pressure medium opening 15 with the valve seat 7 produced, for example, in the stamping process.
  • a compression spring 13 clamped between the stepped valve tappet 5 and the base, the hemispherical valve closing element ⁇ is in its basic position lifted from the valve seat 7.
  • the valve lifter 4 is sectionally along its shaft in the lower and in the upper housing sleeve 5b, 5a, for which purpose the coaxially aligned two valve sleeves 5a, 5b are partially adapted to the outer diameter of the valve lifter 4. Therefore, at the bottom of the upper housing sleeve 5a, a sleeve projection 14 adjoins the inside diameter to the outside diameter of the valve tappet 4, into which the elastic force transmission element 2 also extends to the end face of the valve tappet 4.
  • the rigid force transmission element 2 Located on the elastic force transmission element 3 is the rigid force transmission element 2 designed as a plate, disc or piston, so that the elastic force transmission element 3 is clamped in the manner of a rubber reaction disc between the first force transmission element 2 and the bottom of the housing sleeve 5a.
  • the elastic force transmission element 3 would also be a liquid filling, e.g. Silicone oil or the like conceivable, but this would require sealing measures in the valve housing 5 at the interfaces of the liquid in order to prevent loss of liquid and / or mixing of different liquids.
  • a liquid filling e.g. Silicone oil or the like conceivable, but this would require sealing measures in the valve housing 5 at the interfaces of the liquid in order to prevent loss of liquid and / or mixing of different liquids.
  • valve housing 5 and the cover 24 are simply produced in the illustrated contour by deep-drawing thin sheet metal.
  • FIG. 2 shows a valve which is closed in the basic position, which is realized in an astonishingly simple manner by making minor structural changes to the valve presented in FIG.
  • the arrangement of the valve tappet 4, the two force transmission elements 2, 3 and the piezo element 1 known from FIG. 1 can also be maintained for the valve according to FIG. 2.
  • the cover 24 can also be adopted identically from FIG. 1. It changes only slightly the arrangement of the compression spring 13 and the sleeve projection 14 produced by deep drawing, which is now directed in the opposite direction to the compression spring 13 used in the first force transmission element 2.
  • the first force transmission element 2 is provided as a piston with a central blind bore 18, the bore diameter of which is adapted to the outer diameter of the tappet collar 17 on which the compression spring 13 is supported.
  • the valve tappet 4 consists of a sleeve, the end of which is bent 180 degrees into a tappet collar 17 on a small annular end face of the second force transmission. Bearing element 3 rests, while the winding end of the compression spring 13 directed at the valve tappet 4 rests on the outer radius of the offset.
  • the initiated minimum piezo stroke in the ratio of the acted end faces on the second force transmission element 3 is translated in the sense of an enlarged valve tappet stroke, which is why the ring end face of the second force transmission element 3 which is deformable in the sleeve projection 14 in the direction of the tappet collar 17 is significantly smaller than that of the first force transmission element 2 acted upon ring end face of the second force transmission element 3rd
  • the valve shown considerably enlarged in a sectional illustration in FIG. 3 has a valve tappet 4 which is guided in a valve housing 5 and has a valve closing member 6 at one end.
  • the valve closing member 6 faces a valve seat 7 integrated in the valve housing 5, the valve closing member 6 being actuated indirectly by means of a piezo element 1.
  • a first and a second force transmission element 2, 3 are arranged, the first force transmission element 2 preferably consisting of a metallic material of high strength, which elastically deforms the second force transmission element 3 when the piezo element 1 is electrically activated and moves it in the direction of the valve lifter 4 moves.
  • the contact area A2 of the second force transmission element 3, which is in contact with the end face of the valve tappet 4, is smaller than the contact area A3, which is in contact with the first force transmission element 2, of the second force transmission element which is elastically deformable for stepless translation.
  • the input enables mentioned construction that the second power transmission element 3 seals the hydraulically loaded inner region of the valve housing 5 against the dry inner region of the valve housing 5 in a simple and absolutely safe manner, for which purpose the second force transmission element 3 advantageously made of an elastomer, e.g. B. consists of a commercially available rubber reaction disc or a silicone cushion.
  • the second force transmission element 3 can be pretensioned particularly simply by the choice of the setting depth of the piezo element 1 in the valve housing 5 in order to achieve the required sealing effect of the second force transmission element
  • the piezo element 1 with its end face facing away from the first force transmission element 2, is supported on a compensation piston 8 guided in the valve housing 5, which for the basic setting of the piezo element 1 in the valve housing 5 is acted upon by a rigid plate spring assembly 19, which in turn is inserted into a valve housing 5 Sealing plug 20 is present.
  • the plug 20 is welded, for example, to the upper sleeve section of the valve housing 5.
  • the sealing plug 20 are conceivable.
  • the compensation piston 8 is slidably arranged to compensate for thermally induced changes in volume of the elastic force transmission element 3 between the plate spring assembly 19 and an elastic mass 23 fixed to the bottom of the stepped first housing sleeve 5a.
  • the elastic mass 23 is structurally embedded in a simple manner as a compensating ring 21 in a compensating pot 22, so that commercially available elastomer rings can also be used.
  • the compensating piston 8 is designed in accordance with the geometry of the compensating ring 21 as an annular piston, in the cavity of which the piezo element 1 is received as a stacked piezo block.
  • the first force transmission element 2 is designed as a piston guided along the inner wall of the annular compensation pot 22, which is thus arranged in the vertical direction between the piezo element 1 and the second force transmission element 3.
  • the valve housing 5 ' consists of the two housing sleeves 5a, 5b which are joined together in sections and which are connected to one another in the joining area by means of a welded connection 9.
  • the lower, second housing sleeve 5b is designed as a stepped housing pot, the edge 10 of which is bent at right angles to the outside is caulked in the stepped receiving bore 11 of a block-shaped valve carrier 12.
  • This housing pot has at its bottom a first pressure medium opening 15 with the valve seat 7 produced, for example, in the stamping process.
  • a compression spring 13 clamped between the stepped valve tappet 5 and the base, the hemispherical valve closing member 6 is located in FIG.
  • A2 of the second force transmission element 3 is selected to be substantially smaller than the end face A3 of the second force transmission element 3 acted upon by the first force transmission element 2.
  • the piezo element 1 is arranged between the first force transmission element 2 and an elastically prestressed compensating piston 8, the piston position of which is influenced by the physical properties of the elastic mass 24 fixed in the valve housing 5.
  • the physical property of the elastic mass 23, in particular its temperature-dependent change in volume, therefore corresponds to the physical property of the second force transmission element 3, which is expediently clamped elastically between the first force transmission element 2 and the bottom of the valve housing 5 for linear translation of the piezo stroke.
  • the valve accordingly has a compensating mechanism in order to compensate for the thermal expansion of the elastic force transmission element 3, since the comparatively large coefficient of thermal expansion of the elastomers used for the force transmission element 3 would impair the relatively small valve lift.
  • This temperature-dependent expansion compensation is structurally brought about by the compensation ring 21, which advantageously consists of the material of the elastic force transmission element 3. Due to the thermal expansion of the compensating ring 21, the compensating piston 8 is displaced by the stroke h21 against the rigidly prestressed plate spring assembly 19, as a result of which the thermally induced stroke h3 of the force transmission element 3 is compensated for without causing an undesirable change in the valve stroke h4 which can be achieved by means of the constant mechanical translation ,
  • the volume V2 of the compensating ring 21 is therefore to be set to compensate for the temperature-dependent change in volume on the elastic force transmission element 3 according to the following formula:
  • V2 [VI x (D2 2 -d2 2 )] / Dl 2
  • the two-part valve housing 5 and the compensation pot 22 are simply produced by deep drawing thin sheet metal in the step contour shown.
  • the proposed structure of the valve also enables in the closed position of the valve closing member 6 to sense the hydraulic pressure applied to it, since via the two force transmission elements 2, 3 there is a hydraulic reaction on the piezo element 1, the electrical voltage change resulting from the mechanical pressure stress by means of a electronic evaluation unit is converted into a pressure value.

Abstract

L'invention concerne une soupape, notamment pour des systèmes de freinage à régulation de glissement dans des véhicules à moteur. Cette soupape comprend les éléments suivants : un poussoir (4) de soupape se déplaçant dans une cage de soupape (5), ce poussoir étant doté d'un élément de fermeture de soupape (6) ; un siège (7) de soupape orienté vers l'élément de fermeture de soupape (6) ; un élément piézo-électrique (1) pour actionner l'élément de fermeture de soupape (6). Entre l'élément piézo-électrique (1) et le poussoir (4) se trouvent un premier et un deuxième élément de transmission de force (2, 3). Lors d'une activation électrique de l'élément piézo-électrique (1), le premier élément de transmission de force (2), en matériau de grande résistance, modifie élastiquement la forme du deuxième élément de transmission de force (3) en le poussant vers le poussoir (4).
PCT/EP2002/001385 2001-02-22 2002-02-09 Soupape, notamment pour des systemes de freinage hydrauliques de vehicules WO2002068250A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE50206891T DE50206891D1 (de) 2001-02-22 2002-02-09 Ventil, insbesondere für hydraulische kraftfahrzeug-bremsanlagen
JP2002567584A JP2004526617A (ja) 2001-02-22 2002-02-09 液圧式自動車ブレーキシステム用バルブ
EP02727322A EP1363820B1 (fr) 2001-02-22 2002-02-09 Soupape, notamment pour des systemes de freinage hydrauliques de vehicules
US10/467,730 US7055796B2 (en) 2001-02-22 2002-02-09 Valve, especially for hydraulic automotive brake systems

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE10108522.2 2001-02-22
DE10108522 2001-02-22
DE10117609.0 2001-04-07
DE10117609 2001-04-07
DE10141135.9 2001-08-22
DE10141135A DE10141135A1 (de) 2001-02-22 2001-08-22 Ventil, insbesondere für hydraulische Kraftfahrzeug-Bremsanlagen
DE10141136A DE10141136A1 (de) 2001-04-07 2001-08-22 Ventil.insbesondere für hydraulische Kraftfahrzeugbremsen
DE10141136.7 2001-08-22

Publications (1)

Publication Number Publication Date
WO2002068250A1 true WO2002068250A1 (fr) 2002-09-06

Family

ID=27437937

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2002/001385 WO2002068250A1 (fr) 2001-02-22 2002-02-09 Soupape, notamment pour des systemes de freinage hydrauliques de vehicules

Country Status (5)

Country Link
US (1) US7055796B2 (fr)
EP (1) EP1363820B1 (fr)
JP (1) JP2004526617A (fr)
DE (1) DE50206891D1 (fr)
WO (1) WO2002068250A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1788645A1 (fr) * 2005-11-18 2007-05-23 Delphi Technologies, Inc. Actuateur avec la longueur amplifiée de course
WO2011144642A1 (fr) * 2010-05-17 2011-11-24 Mindray Medical Sweden Ab Vanne à haute pression à commande piézoélectrique et procédé de commande d'une vanne à haute pression

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7717132B2 (en) * 2006-07-17 2010-05-18 Ford Global Technologies, Llc Hydraulic valve actuated by piezoelectric effect
US7841579B2 (en) * 2007-11-01 2010-11-30 Honeywell International Inc. Piezoelectric actuator with a gimballed valve
US7765877B2 (en) * 2007-11-30 2010-08-03 Caterpillar Inc System for preloading piezoelectric actuators and method
SE534897C2 (sv) * 2010-05-17 2012-02-07 Mindray Medical Sweden Ab Piezoelektriskt styrd högtrycksventil samt förfarande för styrning av en högtrycksventil
US20110284779A1 (en) * 2010-05-18 2011-11-24 Mindray Medical Sweden Ab Method and apparatus for controlling a high-pressure valve
JP5421301B2 (ja) * 2011-01-28 2014-02-19 本田技研工業株式会社 バルブ装置
JP5848639B2 (ja) * 2012-03-07 2016-01-27 本田技研工業株式会社 バルブ装置、及び油圧回路の故障検出装置

Citations (5)

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US4762300A (en) * 1985-02-19 1988-08-09 Nippondenso Co., Ltd. Control valve for controlling fluid passage
US4995587A (en) * 1989-11-03 1991-02-26 Martin Marietta Corporation Motion amplifier employing a dual piston arrangement
EP0477400A1 (fr) * 1990-09-25 1992-04-01 Siemens Aktiengesellschaft Dispositif compensateur de tolérance dans la direction de mouvement du transformateur de déplacement d'un dispositif d'actionnement piézoélectrique
DE4119467A1 (de) * 1991-06-13 1992-12-17 Daimler Benz Ag Vorrichtung zur kraft- und hubuebersetzung bzw. -uebertragung
DE19714292A1 (de) * 1997-04-07 1998-10-15 Siemens Ag Vorrichtung zur Übertragung einer Auslenkung eines Aktors

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Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4762300A (en) * 1985-02-19 1988-08-09 Nippondenso Co., Ltd. Control valve for controlling fluid passage
US4995587A (en) * 1989-11-03 1991-02-26 Martin Marietta Corporation Motion amplifier employing a dual piston arrangement
EP0477400A1 (fr) * 1990-09-25 1992-04-01 Siemens Aktiengesellschaft Dispositif compensateur de tolérance dans la direction de mouvement du transformateur de déplacement d'un dispositif d'actionnement piézoélectrique
DE4119467A1 (de) * 1991-06-13 1992-12-17 Daimler Benz Ag Vorrichtung zur kraft- und hubuebersetzung bzw. -uebertragung
DE19714292A1 (de) * 1997-04-07 1998-10-15 Siemens Ag Vorrichtung zur Übertragung einer Auslenkung eines Aktors

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1788645A1 (fr) * 2005-11-18 2007-05-23 Delphi Technologies, Inc. Actuateur avec la longueur amplifiée de course
US7307371B2 (en) 2005-11-18 2007-12-11 Delphi Technologies, Inc. Actuator with amplified stroke length
WO2011144642A1 (fr) * 2010-05-17 2011-11-24 Mindray Medical Sweden Ab Vanne à haute pression à commande piézoélectrique et procédé de commande d'une vanne à haute pression

Also Published As

Publication number Publication date
EP1363820A1 (fr) 2003-11-26
US20040069964A1 (en) 2004-04-15
EP1363820B1 (fr) 2006-05-24
JP2004526617A (ja) 2004-09-02
DE50206891D1 (de) 2006-06-29
US7055796B2 (en) 2006-06-06

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